WO2015005379A1 - Dispositif de verrouillage pour convertisseur de couple - Google Patents

Dispositif de verrouillage pour convertisseur de couple Download PDF

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Publication number
WO2015005379A1
WO2015005379A1 PCT/JP2014/068292 JP2014068292W WO2015005379A1 WO 2015005379 A1 WO2015005379 A1 WO 2015005379A1 JP 2014068292 W JP2014068292 W JP 2014068292W WO 2015005379 A1 WO2015005379 A1 WO 2015005379A1
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WO
WIPO (PCT)
Prior art keywords
inertia
torque converter
damper plate
plate
torque
Prior art date
Application number
PCT/JP2014/068292
Other languages
English (en)
Japanese (ja)
Inventor
裕樹 河原
上原　宏
Original Assignee
株式会社エクセディ
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社エクセディ filed Critical 株式会社エクセディ
Priority to KR1020167000401A priority Critical patent/KR102114792B1/ko
Priority to DE112014003185.2T priority patent/DE112014003185T5/de
Priority to MX2015017344A priority patent/MX2015017344A/es
Priority to CN201480035524.2A priority patent/CN105339706B/zh
Priority to US14/903,597 priority patent/US9732835B2/en
Publication of WO2015005379A1 publication Critical patent/WO2015005379A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1421—Metallic springs, e.g. coil or spiral springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284—Multiple disk type lock-up clutch

Definitions

  • the present invention relates to a lockup device, in particular, a torque converter that is disposed between a front cover coupled to a member on an engine side and a torque converter main body, and directly transmits torque from the front cover to a turbine of the torque converter main body.
  • the present invention relates to a lock-up device.
  • the torque converter is equipped with a lock-up device to reduce fuel consumption.
  • the lockup device is disposed between the turbine and the front cover, and mechanically connects the front cover and the turbine to directly transmit torque between the two.
  • the lockup device generally has a piston and a damper mechanism.
  • the piston is pressed against the front cover by the action of hydraulic pressure, and torque is transmitted from the front cover.
  • the damper mechanism also has a plurality of torsion springs, and the plurality of torsion springs elastically connect the piston and the output-side member connected to the turbine. In such a lockup device, the torque transmitted to the piston is transmitted to the output side member via a plurality of torsion springs and further transmitted to the turbine.
  • Patent Document 1 discloses a lockup device that suppresses fluctuations in the rotational speed of an engine by attaching an inertia member to an output side member.
  • an inertia member is attached to an output member fixed to a turbine so as to be relatively rotatable.
  • a torsion spring as an elastic member is provided between the output member and the inertia member.
  • a torsion spring constituting a dynamic damper device is disposed between a piston and a turbine, and as described above, an annular plate member is elastically attached to an output member via the torsion spring. Connected. And the inertia ring is being fixed to the outer peripheral part of the cyclic
  • An object of the present invention is to provide a dynamic damper device that can occupy a small space especially in the axial direction and can realize cost reduction.
  • a torque converter lock-up device is disposed between a front cover coupled to an engine-side member and a torque converter body, and directly transmits torque from the front cover to a turbine of the torque converter body.
  • the lock-up device includes a clutch portion, an output rotation member, a plurality of first elastic members, and a dynamic damper device.
  • the clutch portion transmits torque from the front cover to the output side.
  • the output rotating member is rotatable relative to the clutch portion and is connected to the turbine.
  • the plurality of first elastic members elastically connect the clutch portion and the output rotation member in the rotation direction.
  • the dynamic damper device is coupled to one of members constituting a power transmission path from the clutch portion to the output rotation member, and attenuates rotational speed fluctuations.
  • the dynamic damper device includes a damper plate, a pair of inertia members, and a plurality of second elastic members.
  • the damper plate has a plurality of first openings extending in the circumferential direction, and rotates together with the output rotating member.
  • Each of the pair of inertia members is disposed on both sides in the axial direction of the damper plate so as to be rotatable relative to the damper plate, and has a second opening extending in the circumferential direction at a position facing the first opening.
  • the plurality of second elastic members are accommodated in the first opening and the second opening, and elastically connect the damper plate and the pair of inertia members.
  • a pair of inertia members are provided on both sides in the axial direction of the damper plate, and the second elastic member is accommodated in the opening of the damper plate and the pair of inertia members. Therefore, compared to the conventional dynamic damper device The space occupied by the dynamic damper device can be reduced.
  • the pair of inertia members can be formed by plate members, and the manufacturing cost can be reduced as compared with the case where the inertia members are formed by casting or forging.
  • the torque converter lockup device is the first side device, wherein the pair of lid members are arranged so as to close the second opening on the axially outer side of the pair of inertia members, respectively. Is further provided.
  • the lid member prohibits the second elastic member from jumping out of the second opening of the pair of inertia members. Moreover, the lid member also functions as a member for increasing the inertia.
  • the lock-up device for a torque converter is the device according to the second aspect, wherein the damper plate has a plurality of elongated holes extending in the circumferential direction between the circumferential directions of the plurality of first openings. ing.
  • the apparatus further includes a connecting member that passes through the long hole in the axial direction and connects the pair of inertia members and the pair of lid members.
  • the connecting member that connects the pair of inertia members and the pair of lid members passes through the long holes of the damper plate.
  • the connecting member functions as a stopper for restricting the relative rotation angle range of the inertia member, the lid member, and the damper plate to a predetermined angle range.
  • the first opening and the long hole of the damper plate are arranged on the same circumference in the device of the third side surface.
  • the inertia member in any of the first to fourth devices, is formed in an annular shape, and the damper plate contacts the inner peripheral surface of the inertia member. It has an inlay portion that contacts and positions the inertia member in the radial direction.
  • an inlay portion is formed in a part of the damper plate, and the inertia member is positioned in the radial direction by the inlay portion.
  • the dynamic damper device in any one of the first to fifth aspects, the dynamic damper device generates the first hysteresis torque in the low rotational speed range, and the medium rotational speed.
  • a hysteresis torque generating mechanism for generating a second hysteresis torque larger than the first hysteresis torque in the region from the region to the high rotational speed region.
  • the rotational speed fluctuation characteristics of the output rotating member change depending on the magnitude of the hysteresis torque.
  • the rotational speed fluctuation of the output rotating member decreases in the low rotational speed region when the hysteresis torque of the dynamic damper device is small, and conversely decreases in the medium rotational speed region when it is large.
  • the hysteresis torque in the dynamic damper device is increased as the rotational speed increases. Therefore, by attaching this dynamic damper device to the lockup device, even when the lockup rotation speed is set to a low rotation speed, fluctuations in the rotation speed can be suppressed in a wide rotation speed range.
  • the lock-up device for a torque converter according to the seventh aspect of the present invention is the device according to the sixth aspect, wherein the hysteresis torque generating mechanism includes a slider and a contact member.
  • the slider rotates together with the inertia member, is movable in the radial direction with respect to the inertia member, and has a sliding surface extending in the rotation direction.
  • the contact member rotates together with the damper plate, and in the low rotation speed range, the relative torsional angle range with the inertia member is restricted to the first angle range by contacting the slider sliding surface.
  • the relative torsional angle range with the inertia member is restricted to the second angular range narrower than the first angular range by contacting the slider sliding surface.
  • a high rotational speed range where the rotational speed is high relative torsion with the inertia member is prohibited by contacting the slider sliding surface.
  • the lock-up device for a torque converter according to the eighth aspect of the present invention is the seventh aspect of the device according to the seventh aspect, wherein a lock portion into which the contact member is fitted is formed at the center of the sliding surface of the slider in the rotational direction. .
  • the lockup device for a torque converter according to the ninth aspect of the present invention further includes an intermediate member in any one of the first to eighth aspects.
  • the intermediate member is rotatable relative to the clutch portion and the output rotating member, and causes at least two of the plurality of first elastic members to act in series.
  • the damper plate is connected to the intermediate member.
  • the damper plate of the dynamic damper device is connected to the intermediate member, and the first elastic member is arranged between the dynamic damper device and the output rotating member. For this reason, even if a member constituting the dynamic damper device has a manufacturing error or the like, a desired torque fluctuation absorption characteristic can be obtained, and fluctuations in rotational speed can be effectively suppressed.
  • the inertia member in the lockup device of the torque converter, it is possible to reduce the occupied space particularly in the axial direction. Further, the inertia member can be formed of a plate member, and the manufacturing cost can be reduced as compared with the case where the inertia member is a cast or forged product.
  • FIG. 3 is a characteristic diagram of engine speed and rotational speed fluctuation.
  • FIG. 3 is a characteristic diagram of engine speed and rotational speed fluctuation.
  • FIG. 1 is a partial sectional view of a torque converter 1 having a lockup device according to an embodiment of the present invention.
  • An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure.
  • OO shown in FIG. 1 is a rotation axis of the torque converter and the lockup device.
  • the torque converter 1 is a device for transmitting torque from an engine-side crankshaft (not shown) to an input shaft of a transmission, and includes a front cover 2 fixed to an input-side member and three types of impellers ( A torque converter main body 6 including an impeller 3, a turbine 4, and a stator 5) and a lockup device 7 are included.
  • the front cover 2 is a disk-shaped member, and an outer peripheral cylindrical portion 10 that protrudes toward the transmission side is formed on the outer peripheral portion thereof.
  • the impeller 3 includes an impeller shell 12 fixed to the outer peripheral cylindrical portion 10 of the front cover 2 by welding, a plurality of impeller blades 13 fixed to the inside thereof, and a cylindrical shape provided on the inner peripheral side of the impeller shell 12. And the impeller hub 14.
  • the turbine 4 is disposed opposite to the impeller 3 in the fluid chamber.
  • the turbine 4 includes a turbine shell 15, a plurality of turbine blades 16 fixed to the turbine shell 15, and a turbine hub 17 fixed to the inner peripheral side of the turbine shell 15.
  • the turbine hub 17 has a flange 17 a extending to the outer peripheral side, and an inner peripheral portion of the turbine shell 15 is fixed to the flange 17 a by a plurality of rivets 18.
  • An input shaft of a transmission (not shown) is splined to the inner peripheral portion of the turbine hub 17.
  • the stator 5 is a mechanism for rectifying the hydraulic oil that is disposed between the impeller 3 and the inner peripheral portion of the turbine 4 and returns from the turbine 4 to the impeller 3.
  • the stator 5 mainly includes a stator carrier 20 and a plurality of stator blades 21 provided on the outer peripheral surface thereof.
  • the stator carrier 20 is supported by a fixed shaft (not shown) via a one-way clutch 22.
  • Thrust bearings 24 and 25 are provided on both axial sides of the stator carrier 20.
  • FIG. 2 shows the lock-up device 7 extracted from FIG.
  • the lockup device 7 is disposed in an annular space between the front cover 2 and the turbine 4.
  • the lockup device 7 includes a clutch portion 28, an outer peripheral side torsion spring (an example of a first elastic member) 29, a float member 30, an intermediate member 31, and an inner peripheral side torsion spring (an example of a first elastic member) 32. And a driven plate (output rotating member) 33 and a dynamic damper device 34.
  • the clutch portion 28 includes a plurality of clutch plates 36, pistons 37, a hydraulic chamber forming member 38, and a drive plate 39.
  • the plurality of clutch plates 36 are disposed between the front cover 2 and the piston 37, and have two first clutch plates 36a and two second clutch plates 36b.
  • the first clutch plate 36a and the second clutch plate 36b are both formed in an annular shape and are arranged alternately in the axial direction.
  • the first clutch plate 36a has a plurality of teeth on the inner periphery.
  • the second clutch plate 36b has friction facings fixed on both sides, and a plurality of teeth are formed on the outer periphery.
  • the piston 37 is formed in an annular shape and is disposed on the transmission side of the front cover 2.
  • a clutch boss 40 is fixed to the inner periphery of the front cover 2.
  • the clutch boss 40 has a flange 40a extending radially outward and a cylindrical portion 40b extending to the axial turbine side.
  • the inner peripheral surface of the piston 37 is supported on the outer peripheral surface of the flange 40a of the clutch boss 40 so as to be movable in the axial direction.
  • a cylindrical portion 37 a that protrudes toward the front cover 2 is formed at a radially intermediate portion of the piston 37.
  • the cylindrical portion 37a is supported by the stepped portion 2a of the front cover 2 so as to be movable in the axial direction.
  • a plurality of openings 37b are formed on the outer peripheral side of the cylindrical portion 37a at predetermined intervals in the circumferential direction.
  • the outer periphery of the piston 37 is disposed so as to face the plurality of clutch plates 36 in the axial direction, and serves as a pressing portion 37c that presses the plurality of clutch plates 36 toward the front cover 2 side.
  • the hydraulic chamber forming member 38 is disposed on the turbine side of the piston 37.
  • the inner peripheral portion of the hydraulic chamber forming member 38 is fixed to the cylindrical portion 40 b of the clutch boss 40.
  • a stepped portion 38 a that forms a cylindrical portion that extends toward the front cover 2 is formed at a radially intermediate portion of the hydraulic chamber forming member 38.
  • a plurality of projecting portions 38 b that project through the opening 37 b of the piston 37 and project to the front cover 2 side are formed on the outer peripheral portion of the stepped portion 38 a.
  • the plurality of protruding portions 38b are formed at predetermined intervals in the circumferential direction, and teeth formed on the inner peripheral portion of the first clutch plate 36a are engaged with the protruding portions 38b. Therefore, the first clutch plate 36a and the hydraulic chamber forming member 38 are relatively unrotatable and relatively movable in the axial direction.
  • an extended portion 38c is formed on the outer peripheral portion of the hydraulic chamber forming member 38 so as to extend outward in the radial direction.
  • the extension portion 38 c covers the turbine side of the piston 37 and the clutch plate 36.
  • seal members 42 and 43 are provided on the outer peripheral surface of the flange 40 a of the clutch boss 40 and the stepped portion 2 a of the front cover 2. Thereby, the space between the inner peripheral surface of the piston 37 and the clutch boss 40 and the space between the cylindrical portion 37a of the piston 37 and the stepped portion 2a of the front cover 2 are sealed, and the first oil chamber 44a for clutch-off is formed. Is formed. Further, a seal member 45 is provided on an annular projecting portion 37d projecting to the turbine 4 side of the piston 37. Thereby, the space between the piston 37 and the hydraulic chamber forming member 38 is sealed, and a second oil chamber 44b for clutch-on is formed.
  • the clutch boss 40 is formed with a first oil passage 40c communicating with the first oil chamber 44a and a second oil passage 40d communicating with the second oil chamber 44b.
  • the drive plate 39 is provided on the output side of the clutch portion 28. Specifically, the drive plate 39 is provided on the outer peripheral side of the clutch plate 36.
  • the drive plate 39 has a clutch engaging portion 39a extending to the front cover 2 side and a plurality of spring engaging portions 39b.
  • the clutch engaging portion 39a is formed in a cylindrical shape, and grooves extending in the axial direction are formed at predetermined intervals in the circumferential direction. And the tooth
  • the plurality of spring engaging portions 39 b extend radially outward from the turbine side of the clutch engaging portion 39 a and are engaged with both end surfaces of the outer peripheral side torsion spring 29.
  • a plurality of claws 39d extending to the turbine side are formed in a portion 39c between the clutch engaging portion 39a and the spring engaging portion 39b.
  • the plurality of outer peripheral side torsion springs 29 are composed of, for example, a total of eight springs in one set, and the float member 30 is provided so that the two outer peripheral side torsion springs 29 of each set act in series. Yes.
  • the float member 30 is an annular member having a C-shaped cross section, and is disposed above the clutch engagement portion 39a of the drive plate 39.
  • the float member 30 is disposed so as to be rotatable relative to the drive plate 39, and the outer peripheral portion supports the outer peripheral portion of the outer peripheral torsion spring 29, and the side portion supports the engine-side side portion of the outer peripheral side torsion spring 29. is doing. That is, the float member 30 restricts the outer peripheral side torsion spring 29 from protruding outward and laterally.
  • a front end portion of the float member 30 on the transmission side in the axial direction is bent toward the inner peripheral side and the engine side, and a bent portion 30 a of the front end portion is inserted between a pair of outer peripheral side torsion springs 29. That is, both end surfaces in the circumferential direction of the bent portion 30 a are in contact with the end surfaces of the corresponding outer peripheral torsion springs 29.
  • both ends in the circumferential direction of the set of outer peripheral side torsion springs 29 arranged so as to act in series are engaged with the clutch engaging portions 39a of the drive plate 39, and the set of outer peripheral side torsion springs 29
  • the bent portion 30a of the float member 30 is inserted in the middle portion. Further, the outer peripheral portion of the outer peripheral side torsion spring 29 is supported by the outer peripheral portion of the float member 30.
  • FIG. 3 shows the intermediate member 31 and the dynamic damper device 34 extracted from FIG.
  • the intermediate member 31 includes a first plate 48 and a second plate 49 and is rotatable relative to the drive plate 39 and the driven plate 33.
  • the first and second plates 48 and 49 are annular and disk-shaped members disposed between the clutch portion 28 and the turbine shell 15.
  • the first plate 48 and the second plate 49 are arranged with an interval in the axial direction.
  • the first plate 48 is disposed on the engine side, and the second plate 49 is disposed on the transmission side.
  • the outer periphery of the first plate 48 and the second plate 49 is connected to each other by a plurality of rivets 50 so that they cannot rotate relative to each other and cannot move in the axial direction.
  • the first plate 48 and the second plate 49 are formed with windows 48a and 49a penetrating in the axial direction, respectively.
  • the window portions 48a and 49a are formed extending in the circumferential direction, and cut-and-raised portions cut and raised in the axial direction are formed on the inner and outer peripheral portions.
  • a plurality of locking portions 48 b extending to the outer peripheral side torsion spring 29 are formed on the outer peripheral end of the first plate 48.
  • the plurality of locking portions 48b are formed by bending the front end of the first plate 48 toward the axial engine side.
  • the plurality of locking portions 48b are arranged at a predetermined interval in the circumferential direction, and a pair of outer peripheral side torsion springs 29 acting in series are arranged between the two locking portions 48b. Yes.
  • the outer peripheral side torsion spring 29 and the inner peripheral side torsion spring 32 can be caused to act in series.
  • holes 48c and 49c penetrating in the axial direction are formed in the outer peripheral portions of the first and second plates 48 and 49.
  • a claw 39d of the drive plate 39 is inserted into the holes 48c and 49c.
  • a hole penetrating in the radial direction is formed in the claw 39d, and a part of the leaf spring 51 whose one end is fixed to the rivet 50 is engaged with the hole of the claw 39d.
  • Each of the plurality of inner peripheral side torsion springs 32 includes a combination of a large coil spring and a small coil spring inserted into the large coil spring and having the same length as the spring length of the large coil spring.
  • Each inner peripheral side torsion spring 32 is disposed in the windows 48 a and 49 a of both plates 48 and 49 of the intermediate member 31.
  • Each inner torsion spring 32 is supported at both ends in the circumferential direction and both sides in the radial direction by the windows 48a and 49a. Furthermore, each inner peripheral side torsion spring 32 is restricted from projecting in the axial direction by the cut and raised portions of the windows 48a and 49a.
  • the driven plate 33 is an annular and disk-shaped member, and an inner peripheral portion thereof is fixed to the flange 17 a of the turbine hub 17 by a rivet 18 together with the turbine shell 15.
  • the driven plate 33 is disposed between the first plate 48 and the second plate 49 so as to be rotatable relative to both the plates 48 and 49.
  • a window hole 33 a is formed in the outer peripheral portion of the driven plate 33 corresponding to the window portions 48 a and 49 a of the first and second plates 48 and 49.
  • the window hole 33a is a hole penetrating in the axial direction, and the inner peripheral torsion spring 32 is disposed in the window hole 33a.
  • the dynamic damper device 34 includes a damper plate 52 that is an outer peripheral extension portion of the second plate 49 of the intermediate member 31, a pair of inertia rings 53, and a pair of inertia rings 53.
  • the lid member 54 includes a plurality of coil springs (second elastic members) 55 and a stop pin 56.
  • FIG. 4 is a partial view of the dynamic damper device 34 viewed from the front cover 2 side.
  • FIG. 5 is a cross-sectional view taken along the line VV in FIG.
  • the damper plate 52 is a portion formed by extending the outer periphery of the second plate 49 constituting the intermediate member 31.
  • a plurality of damper plates 52 are provided at predetermined intervals in the circumferential direction.
  • the spring storage portion 52a is formed with a predetermined length in the circumferential direction.
  • a plurality of long holes 52b are formed between the circumferential directions of the plurality of spring storage portions 52a.
  • the long hole 52b has a predetermined length in the circumferential direction, and is formed on the same circumference as the spring storage portion 52a.
  • a plurality of spigot portions 52c are formed between the spring housing portion 52a and the long hole 52b in the circumferential direction.
  • the inlay portion 52c is formed by cutting and raising a part of the damper plate 52 to the front cover 2 side.
  • the pair of inertia rings 53 are formed by pressing a sheet metal member, and are disposed on both sides of the damper plate 52 in the axial direction.
  • the two inertia rings 53 have the same configuration.
  • the inertia ring 53 has a plurality of spring storage portions (second openings) 53a at predetermined intervals in the circumferential direction.
  • the spring storage portion 53 a is formed at a position corresponding to the spring storage portion 52 a of the damper plate 52.
  • the inertia ring 53 has a through hole 53 b at a position corresponding to the center position in the circumferential direction of the long hole 52 b of the damper plate 52.
  • the pair of lid members 54 are disposed outside the pair of inertia rings 53 in the axial direction. Specifically, one lid member 54 is further disposed on the front cover 2 side of the inertia ring 53 disposed on the front cover 2 side, and the other lid member 54 is further disposed on the inertia ring 53 disposed on the turbine 4 side. It is arranged on the turbine 4 side.
  • the lid member 54 is formed in an annular shape, and the inner and outer diameters are the same as the inner and outer diameters of the inertia ring 53.
  • a through hole 54 b is formed in the lid member 54 at a position corresponding to the through hole 53 b of the inertia ring 53.
  • a concave portion 54c having a diameter larger than that of the through hole 54b is formed at an end portion on the axially outer side of the through hole 54b.
  • the plurality of coil springs 55 are housed in the spring housing portion 52a of the damper plate 52 and the spring housing portion 53a of the inertia ring 53, respectively. Both end portions of the coil spring 55 are in contact with the end portions in the circumferential direction of the spring accommodating portions 52 a and 53 a of the damper plate 52 and the inertia ring 53.
  • the stop pin 56 has a large-diameter barrel portion 56 a at the axial center portion and small-diameter barrel portions 56 b on both sides thereof.
  • the large-diameter trunk portion 56 a has a larger diameter than the through-hole 53 b of the inertia ring 53 and a smaller diameter than the diameter (diameter direction dimension) of the long hole 52 b of the damper plate 52. Further, the thickness of the large-diameter trunk portion 56 a is formed slightly thicker than the thickness of the damper plate 52.
  • the small-diameter body portion 56b is inserted through the through hole 53b of the inertia ring 53 and the through hole 54b of the lid member 54. And the inertia ring 53 and the cover member 54 are being fixed to the axial direction both sides of the damper plate 52 by crimping the head of the small diameter trunk
  • the damper plate 52, the inertia ring 53, and the lid member 54 can be relatively rotated within a range in which the stop pin 56 can move through the long hole 52b of the damper plate 52. And when the large diameter trunk
  • the inner peripheral surface of the inertia ring 53 abuts on the outer peripheral surface of the spigot portion 52c of the damper plate 52, whereby the inertia ring 53, the lid member 54 and the coil spring 55 are positioned in the radial direction.
  • the lockup device 7 transmits torque and absorbs and attenuates torque fluctuations input from the front cover 2. Specifically, when torsional vibration occurs in the lockup device 7, the outer peripheral side torsion spring 29 and the inner peripheral side torsion spring 32 are compressed in series between the drive plate 39 and the driven plate 33. Furthermore, also in the outer peripheral side torsion spring 29, one set of outer peripheral side torsion springs 29 is compressed in series. For this reason, the twist angle can be widened. In addition, since the outer peripheral side torsion spring 29 that can take a long distance in the circumferential direction acts in series, a wider twist angle can be secured. This means that the torsional characteristics can be further reduced in rigidity, and vibration absorption / damping performance can be further improved.
  • the dynamic damper device 34 is fixed to the intermediate member 31, and the inner peripheral torsion spring 32 for suppressing vibration is disposed between the dynamic damper device 34 and the turbine hub 17. Due to the action of the inner periphery side torsion spring 32, as shown in FIG. 8, fluctuations in rotational speed can be more effectively suppressed.
  • the characteristic C1 shows the rotational speed fluctuation in the conventional lockup device.
  • Characteristic C2 shows the fluctuation when the dynamic damper device is mounted on the turbine hub and there is no elastic member (torsion spring) on the output side of the dynamic damper device.
  • the characteristic C3 shows the fluctuation when the dynamic damper device is mounted on the intermediate member and the elastic member (inner peripheral side torsion spring 32) is provided on the output side of the dynamic damper device as in the present embodiment.
  • the pair of inertia rings 53 are arranged on both sides of the damper plate 52 to constitute the dynamic damper device 34, the pair of inertia rings 53 can be formed of a plate member. Therefore, the manufacturing cost can be reduced as compared with the case where the inertia ring is formed of a cast product or a forged product.
  • the cover member 54 prohibits the coil spring 55 from jumping out of the spring housing 53 a of the inertia ring 53. For this reason, it is not necessary to provide the inertia ring 53 with a projection or the like for restricting the spring of the coil spring 55 from protruding. Further, the lid member 54 can be used as inertia.
  • An inlay portion 52c is provided on the damper plate 52 to position the inertia ring 53 and the lid member 54 in the radial direction. Therefore, the dynamic damper device 34 can be positioned in the radial direction with a simple configuration.
  • the shape of the pair of inertia rings is the same, but the shapes may be different from each other.
  • the damper plate is formed on the outer peripheral portion of the second plate of the intermediate member.
  • the damper plate may be provided as a separate member.
  • a hysteresis torque generating mechanism may be provided in the dynamic damper device in the embodiment.
  • FIG. 9 shows the hysteresis torque generating mechanism 60.
  • the thickness of one (or both) of the pair of inertia rings 61 is thicker than that of the above-described embodiment.
  • a hysteresis torque generating mechanism 60 is incorporated in the inertia ring 61.
  • the hysteresis torque generating mechanism 60 is a mechanism that generates a variable hysteresis torque between the damper plate 62 (see FIG. 10) and the inertia ring 61.
  • the hysteresis torque generating mechanism 60 has a claw 62d of a damper plate 62, a slider 63, and a spring 64 as shown in FIG.
  • the damper plate 62 is a part formed by extending the outer periphery of the second plate constituting the intermediate member, as described above, but may be formed by another member.
  • the basic configuration of the damper plate 62 is the same as that of the above embodiment except that the claws 62d are formed. That is, it has the spring accommodating part 62a, the long hole 62b, and the spigot part 62c, and the function of these each part is the same as that of the said embodiment.
  • the damper plate 62 has a claw 62d. Specifically, a plurality of notches 62e are formed in a predetermined angle range on the outer peripheral portion of the damper plate 62, and the central portion in the circumferential direction is formed at the inner peripheral edge of the notch 62e. Claws 62d are formed by bending toward the inertia ring 61 side.
  • the inertia ring 61 is an annular member and is disposed so as to be rotatable relative to the damper plate 62.
  • the inertia ring 61 includes a plurality of spring storage portions 61a, through holes 61b through which stop pins are inserted, and a slider storage portion 61c at predetermined intervals in the circumferential direction.
  • the plurality of coil springs 55 are housed in the spring housing portion 62 a of the damper plate 62 and the spring housing portion 61 a of the inertia ring 61.
  • this coil spring 55 the damper plate 62 and the inertia ring 61 are elastically connected in the rotational direction.
  • the slider 63 is a member that extends long in the circumferential direction, and is housed in a slider housing portion 61 c of the inertia ring 61 so as to be movable in the radial direction.
  • FIG. 12 shows the slider storage portion 61c and the slider 63 of the inertia ring 61 extracted.
  • the slider storage portion 61c has spring receiving portions 61d at both ends in the circumferential direction.
  • the walls at both ends in the circumferential direction of the slider storage portion 61c function as guide portions 61e.
  • the slider 63 has spring accommodating portions 63a formed radially inward at both ends in the circumferential direction.
  • Each spring accommodating portion 63a accommodates a spring 64 that urges the slider 63 toward the inner peripheral side. Both ends in the longitudinal direction of the slider 63 are slidably in contact with the guide portion 61e of the slider storage portion 61c.
  • the outer peripheral surface 63b of the slider 63 is curved so as to be recessed inward.
  • a lock portion 63c into which the claw 62d of the damper plate 62 is fitted is formed at the central portion of the outer peripheral surface 63b in the circumferential direction.
  • the rotational speed fluctuation of the turbine with respect to the rotational speed fluctuation E1 of the engine has characteristics as shown by curves E2 and E3 depending on the magnitude of the hysteresis torque in the hysteresis torque generating mechanism 60. Both characteristics E2 and E3 are characteristics when a dynamic damper device is provided.
  • Characteristic E2 is when the hysteresis torque is relatively large, and characteristic E3 is when the hysteresis torque is relatively small.
  • the rotational speed fluctuation of the turbine is small when the engine speed is lower than 1200 rpm, becomes maximum near 1500 rpm, and gradually decreases when the engine speed is higher.
  • the rotational speed fluctuation of the turbine shows a minimum value smaller than the characteristic E2 when the engine speed exceeds 1200 rpm, and becomes the maximum exceeding the characteristic E2 near 1600 rpm.
  • the rotational speed fluctuation of the turbine is smaller when the hysteresis torque is smaller in the engine speed range where the engine speed is low, and is smaller when the hysteresis torque is greater in the intermediate speed range. Further, in the high rotation speed range, the influence of the hysteresis torque on the turbine rotation speed fluctuation is small.
  • the hysteresis torque generating mechanism 60 is configured such that the hysteresis torque changes depending on the rotation speed range. Specifically, the hysteresis torque generated by the hysteresis torque generating mechanism 60 is small in the region where the engine speed is low, and gradually increases in the middle and high speed regions.
  • the centrifugal force acting on the slider 63 is relatively small in the low rotational speed range. For this reason, as shown in ⁇ normal time> of FIG. 14A, the slider 63 is biased toward the inner peripheral side by the biasing force of the spring 64. In such a state, when the dynamic damper device operates and the damper plate 62 and the inertia ring 61 rotate relative to each other, the claws 62d of the damper plate 62 relatively move on the outer peripheral side of the outer peripheral surface 63b of the slider 63.
  • the angular range (torsion angle) of the relative rotation of the damper plate 62 is regulated by the claw 62 d coming into contact with the outer peripheral surface 63 b of the slider 63.
  • the torsion angle is the maximum ⁇ 1.
  • the claw 62d smoothly moves outward from the slider 63, so the hysteresis torque in this case is small.
  • the claw 62d strongly contacts the outer peripheral surface 63b of the slider 63, so that a hysteresis torque larger than the hysteresis torque in the low rotational speed region is generated.
  • the slider 63 When the rotational speed is further increased, the slider 63 further moves toward the outer periphery against the urging force of the spring 64 and becomes in a state as shown in ⁇ at the time of locking> in FIG. In this state, the claw 62 d is fitted into the lock portion 63 c of the outer peripheral surface 63 b of the slider 63. That is, the relative rotation between the claw 62d (that is, the damper plate 62) and the inertia ring 61 is prohibited and locked. For this reason, in the state shown in FIG.14 (c), the hysteresis torque in a dynamic damper apparatus becomes infinite.
  • the characteristic of the turbine rotational speed fluctuation is the characteristic E3 in the low rotational speed range and the characteristic E2 in the middle rotational speed range to the high rotational speed range as shown in FIG. For this reason, the turbine rotational speed fluctuation can be kept small in the entire engine speed range.
  • the dynamic damper device is fixed to the intermediate member that connects the outer peripheral side torsion spring and the inner peripheral side torsion spring, but the arrangement of the dynamic damper device is not limited to this.
  • the dynamic damper device may be fixed to a float member for causing two outer peripheral torsion springs to act in series.
  • the dynamic damper device may be fixed to a member for causing the two inner peripheral side torsion springs to act in series.
  • a torsion spring as a damper mechanism on the output side of the dynamic damper device, secondary resonance can be suppressed.
  • the configuration for connecting the dynamic damper device to the intermediate member is not limited to the configuration of the above embodiment.
  • teeth, claws, and notches may be formed on the intermediate member and the member constituting the dynamic damper device, and both may be connected.
  • the elastic member is constituted by a coil spring, but an elastic member made of other resin or the like may be used.
  • the occupied space in the axial direction can be reduced.
  • the inertia member can be formed of a plate member, and the manufacturing cost can be reduced as compared with the case where the inertia member is a cast or forged product.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un dispositif amortisseur dynamique qui occupe peu d'espace dans la direction axiale et qui peut être conçu de manière à présenter un poids léger. Le dispositif comprend une partie d'embrayage (28), une plaque entraînée (33), une pluralité de ressorts de torsion (29, 32) et un dispositif amortisseur dynamique (34). Le dispositif amortisseur dynamique (34) comprend une plaque d'amortissement (52), une paire de bagues d'inertie (53) et une pluralité de ressorts hélicoïdaux (55). La plaque d'amortissement (52) comprend une pluralité de parties de logement de ressort (52a). Les bagues d'inertie (53) sont agencées sur des côtés respectifs, dans la direction axiale, de la plaque d'amortissement (52) de manière à être rotatives par rapport à la plaque d'amortissement (52) et comprennent chacune des parties de logement de ressort (53a). La pluralité de ressorts hélicoïdaux (55) est logée dans les parties de logement de ressort respectives (52a, 53a) et accouple de manière élastique la plaque d'amortissement (52) à la paire de bagues d'inertie (53).
PCT/JP2014/068292 2013-07-11 2014-07-09 Dispositif de verrouillage pour convertisseur de couple WO2015005379A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
KR1020167000401A KR102114792B1 (ko) 2013-07-11 2014-07-09 토크 컨버터의 록업 장치
DE112014003185.2T DE112014003185T5 (de) 2013-07-11 2014-07-09 Überbrückungsvorrichtung für einen Drehmomentwandler
MX2015017344A MX2015017344A (es) 2013-07-11 2014-07-09 Dispositivo de cerradura para convertidor de par motor.
CN201480035524.2A CN105339706B (zh) 2013-07-11 2014-07-09 液力变矩器的锁定装置
US14/903,597 US9732835B2 (en) 2013-07-11 2014-07-09 Lockup device for torque converter

Applications Claiming Priority (2)

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JP2013145452A JP5878893B2 (ja) 2013-07-11 2013-07-11 トルクコンバータのロックアップ装置
JP2013-145452 2013-07-11

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WO2015005379A1 true WO2015005379A1 (fr) 2015-01-15

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US (1) US9732835B2 (fr)
JP (1) JP5878893B2 (fr)
KR (1) KR102114792B1 (fr)
CN (1) CN105339706B (fr)
DE (1) DE112014003185T5 (fr)
MX (1) MX2015017344A (fr)
WO (1) WO2015005379A1 (fr)

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JP2017083004A (ja) * 2015-10-30 2017-05-18 株式会社ユタカ技研 トルクコンバータ
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US20180112758A1 (en) * 2015-05-20 2018-04-26 Exedy Corporation Lock-up device for torque converter
US10047845B2 (en) 2016-01-14 2018-08-14 Valeo Embrayages Dynamic absorber for torsional vibration damper of hydrokinetic torque coupling device
US10054208B2 (en) 2015-12-07 2018-08-21 Valeo Embrayages Frequency dynamic absorber for torsional vibration damper of hydrokinetic torque coupling device
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DE112014003185T5 (de) 2016-03-31
CN105339706A (zh) 2016-02-17
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US9732835B2 (en) 2017-08-15
CN105339706B (zh) 2017-11-14

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